Compressible fluid contact heat exchanger

ABSTRACT

This invention is directed to the contact interchange of thermal and kinetic energy between adjacent compressible fluid streams across a virtual heat transfer surface at substantially different velocities in parallel flow. The invention may find especial application as a regenerative heat exchanger in gas turbine power plants, or as the low-velocity contact-type air pre-heater of a steam generator or furnace. Hot low-pressure exhaust fluids and cool compressed intake fluids enter the receiver-side section of an elongate heat exchanger. Intake-fluid stream pressure energy is converted to kinetic energy within nozzle passageways of the receiver-side section. The cold high-velocity intake-fluid stream is rapidly heated in the velocity-accelerated contact interchange process by the hot low-velocity exhaust-fluid stream within the mixing section. Following the contact interchange process, the intakefluid and exhaust-fluid streams are separated from each other by flow-dividing members and discharged from the separator-side section. Within the preheated intake-fluid stream, normal shock in supersonic flow across the inlet of the intake-fluid discharge passage is averted by the effects of variable control over characteristic length and exhaust-fluid outlet flow control.

United States Patent [1 1 Hull [ COMPRESSIBLE FLUID CONTACT HEATEXCHANGER [76] Inventor: Francis R. Hull, 567 E. 26th St.,

Brooklyn, NY. 11210 221 Filed: Jan. 27, 1971 211 Appl. No.: 110,046

Related US. Application Data [63] Continuation-impart of Ser. Nos.830,189, May 19, 1969, abandoned, and Ser. No. 689,241, Nov. 29, 1967,abandoned, and Ser. No. 632,122, Feb. 6, 1967, abandoned, and Ser. No.562,068, June 1, 1966, abandoned, and Ser. No. 323,499, Nov. 13, 1963,abandoned.

[52] US. Cl 165/111; 60/3951 R; 165/1; 165/52; 165/96 [51] Int. Cl. F28c3/02 [58] Field 01 Search 165/1, 52, 96, 155, 164, 165/111; 60/3951 R,95

[56] References Cited FOREIGN PATENTS OR APPLICATIONS 869,355 5/1961United Kingdom 165/1 Primary ExaminerAlbert W. Davis, Jr.

[ 1 Oct. 28, 1975 [57] ABSTRACT This invention is directed to thecontact interchange of thermal and kinetic energy between adjacentcompressible fluid streams across a virtual heat transfer surface atsubstantially different velocities in parallel flow. The invention mayfind especial application as a regenerative heat exchanger in gasturbine power plants, or as the low-velocity contact-type air preheaterof a steam generator or furnace.

Hot low-pressure exhaust fluids and cool compressed intake fluids enterthe receiver-side section of an elongate heat exchanger. Intake-fluidstream pressure energy is converted to kinetic energy within nozzlepassageways of the receiver-side section. The cold high-velocityintake-fluid stream is rapidly heated in the velocity-acceleratedcontact interchange process by the hot lowvelocity exhaust-fluid streamwithin the mixing section. Following the contact interchange process.the intake-fluid and exhaust-fluid streams are separated from each otherby flow-dividing members and discharged from the separator-side section.Within the preheated intake-fluid stream, normal shock in supersonicflow across the inlet of the intake-fluid discharge passage is avertedby the effects of variable control over characteristic length andexhaust-fluid outlet flow control.

26 Claims, 39 Drawing Figures U.S. Patent Oct.28, 1975 Sheet 1 of 103,915,222

Franc/Is R Hall INVENTOR iiii l1- arm ATTORNEY U.S. Patent 0m. 28, 1975Sheet 2 of 1 3,915,222

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Franc/Is R Hu/l INVENTOR ATTORNEY US. Patent Oct. 28, 1975 R 56ENERATIVE APARAT U? Sheet 3 of 10 FIG 8 I OI -95 GENERATOR TURBINE FLOWCOMPRESSOR 66 GAS REGENERATIVE APARATUS 3 FREE 57 TURBINE COMBUSTION 64I HAMBER 67 7/ n nEsson 65 70 GAS GENERATOR TURBINE Bl #271212 R Hul/ATTOR N EY U.S. Patent Oct.28, 1975 Sheet6of 10 3,915,222

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INVENTOR. F rancis R. Hull BY Z46- $63M;

ATTORNEYS U.S. Patent Oct.28, 1975 Sheet8of 10 3,915,222

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ATTORNEYS US. Patent 061.28, 1975 Sheet 10 of 10 3,915,222

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cu E7 m P3 LL. m Q m m m N N m (\1 L0 g 0 m m (D R, m m U! m a: 8 LLINVENTOR. Francis R. Hull ATTORNEY COMPRESSIBLE FLUID CONTACT HEATEXCHANGER The present invention is acontinuation-in-part of my presentlypending application Ser. No. 830,189, entitled Compressible FluidContact Heat Exchanger filed May 19, 1969, now abandoned; my priorapplication Ser. No. 689,241 entitled Compressible Fluid Contact HeatExchanger" filed Nov. 29, 1967, now abandoned; my prior application Ser.No. 632,122 entitled Compressible Fluid Contact Heat Exchanger" filedFeb. 6, 1967, now abandoned; my prior application Ser. No. 562,068entitled Compressible Fluid Contact Heat Exchanger" filed June I, 1966,now abandoned; and my prior application Ser. No. 323,499 entitledCompressible Fluid Contact Heat Exchanger" filed Nov. 13, 1963, nowabandoned.

This invention relates to the contact interchange of thermal energybetween adjacent streams of compressible fluids at different velocitiesin parallel flow by means of opposed sonic or super-sonicnozzle-diffuser combinations and arrangements, the entire nozzledifluserassemblage being concentrically mounted within the confines of a duct ortubular accommodating and mixing chamber.

As used hereinafter,

The term fluid shall refer to any liquid or gaseous medium;

The term compressible fluid shall refer to any gaseous medium; the termexhaust fluid shall refer to the discharge stream of combusted gasesfrom an internal combustion engine, to the exhaust gases from any otherheat engine, or to high-temperature gases leaving a combustion chamberor other heat source;

the term intake fluid shall relate to the incoming fluid stream ofprecombustion gases to an internal combustion engine (air), the incomingfluid stream to a heat engine, the incoming fluid stream to thecombustion chamber of any heat exchange apparatus, or to the incomingfluid stream to any other heat source before major quantities of thermalenergy are added to the incoming fluid stream;

the term heat engine shall refer to a thermodynamic engine which mayconvert thermal or molecular energy in the working fluid stream tomechanical energy, or convert mechanical energy to thermal or molecularenergy in the working fluid stream;

the term contact interchange shall relate to the fluid'to-fluid exchangeof thermal and kinetic energy between adjacent fluid streams havingdifferent velocities in parallel flow, and having now phys ical ormechanical separation between them;

the term heating fluid shall refer to the lowtemperature member ofadjacent fluid streams in parallel flow which is being heated by contactinterchange with an adjacent hightemperature fluid stream;

the term coming fluid shall relate to the hightemperature 1ember ofadjacent fluid streams wh ch is being cooled by contact interchange withan adjacent low-temperature fluid stream;

the term combusted fluid shall refer to a fluid stream within which acombustion process has taken place following the injection ofacombustible fuel;

the term sub-sonic flow shall refer to fluid velocities which are lessthan the velocity of sound in the fluid at a particular energy state;

the term sonic flow shall refer to fluid velocities which are equal tothe velocity of sound in the fluid at a particular energy state;

the term super-sonic flow shall refer to fluid velocities which aregreater than the velocity of sound in the fluid at a particular energystate;

the term mixing length shall refer to the effective linear dimensionperpendicular to the direction of mean fluid flow within which contactinterchange of thermal and kinetic energy shall take place between aheating fluid stream and a cooling fluid stream;

the term characteristic length shall refer to the effective lineardimension parallel to the direction of mean fluid flow within whichenergy transfer be tween particles of adjacent heating fluid and coolingfluid streams shall take place by means of contact interchange;

the term regenerator shall refer to a device which transfers thermalenergy from hot exhaust gases in a thermal process or cycle to coolerintake fluids normally a part of the same process or cycle;

the term atmospheric gas-turbine regenerator shall relate to a devicewhich partially recovers thermal energy from hot gas turbine exhaustgases that would otherwise be lost on discharge to the atmosphere, bytransfer to this themral energy so as to pre-heat the intake air-fluidstream;

the term purge system shall relate to mechanical means of varying thecross-sectional throat area of an atmospheric exhaust nozzle so as topermit periodically a temporary increase of throat area and so permit anincreased discharge from the exhaust nozzle, resulting in a consequentreduction of combustion products concentration within the heating fluidintake stream in fluid system branches downstream of the apparatus ofthe invention which may be caused by recirculation of entrainedcombustion products.

While the apparatus of the invention is described in connection with gasturbine exhaust energy recovery for the purpose of improving the powerplant thermal efficiency of gas turbine plants exhausting to atmosphericpressures, it will be understood by those skilled in the art thatsimilar structures may be employed in connection with other apparatuswhere regeneration by means of contact interchange between adjacentfluid .eams at different initial pressure is desired.

The primary object of the invention is to provide a r eans ofcomparatively simple construction whereby tnermal energy present in theexhaust fluid stream of a heat engine, such as a gas turbine, may bepartially recovered by means of contact interchange with the cooler,higher-pressure intake fluid stream to the engine.

Another object is the provision of practicable means of contactinterchange between the exhaust and intake fluid streams of a gasturbine power plant so as to preheat the intake fluid stream before itenters the combustion chamber or other heat source, thereby decreasingfuel consumption and increasing power plant thermal efficiency.

Another object is to provide a practicable means of achieving contactinterchange which will accelerate transfer of thermal energy toconditions approaching thermal equilibrium between the exhaust andintake fluid streams ofa gas turbine, or other heat engine, heat source,or thermal process.

Still another object of the invention is to provide a physicallyfeasible means of effecting contact interchange of thermal and kineticenergy between adjacent fluid streams which are at substantiallydifferent initial pressures.

A further object is to achieve a regenerator configuration ofcomparatively simple construction and compact design which will besuitable for use in connection with mobile gas turbine power plants, andfor compact, light-weight gas turbine power plants which may beinstalled as a fixed installation in remote areas.

With the foregoing objects in view, together with others which willappear as the description proceeds, the invention resides in the novelconstruction, assemblage, and arrangement of parts which will bedescribed more fully in the discussion illustrated in the drawings, andparticularly pointed out in the claims.

In the drawings:

FIG. I is a fragmentary longitudinal sectional view through an apparatuswhich involves the teachings of the present invention, the same beingshown in the form of a gaseous contact heat exchanger, which isinstalled as part of the apparatus of a gas turbine power plantexhausting to atmospheric pressures for the purpose of effecting anexchange and transfer of thermal energy between the hot, low-pressuregases exhausted from the turbine and the cooler, higher-pressure fluidstream of incoming air being received from a compressor.

FIG. 2 is an exterior end view of the apparatus illustrated in FIG. I.

FIG. 3 is a transverse sectional view along line 3-3 of FIG. I.

FIG. 4 is a transverse sectional view along line 44 of FIG. 1.

FIG. 5 is a schematic sectional diagram of a pistonactuated purgecontrol system for periodically lessening combustion productsconcentration within fluid system branches downstream of the apparatusof the invention. by a mechanical variation ofthe cross-sectional flowarea of an atmospheric exhaust nozzle throat. The purge controlapparatus is shown schematically in the extended, or normal operatingposition.

FIG. 6 is a schematic sectional diagram of the pistonactuated purgecontrol means of FIG. 5 when it is in the retracted, or purge operatingposition.

FIG. 7 is a schematic process diagram of a gas turbine power plant whichincorporates the apparatus of the illustrative embodiment within itsflow processes in a conventional manner.

FIG. 8 is a schematic process diagram of a gas turbine power plant whichincorporates the apparatus of the illustrative embodiment within itsflow processes in an unconventional manner which segregates thecombustion process from the power generating process.

FIG. 9 is a schematic sectional diagram of the throat piece operatinglinkage of FIGS. 5 and 6 when it is actuated by a handoperated powerscrew. This control means may be used to adjust exhaust nozzle throatpressure to ambient atmospheric pressure without purging for powersystems and processes which do not produce solid products of combustionin their combus tion process.

FIG. 10 is a fragmentary longitudinal sectional view through anapparatus having the same application and purpose as the apparatus ofFig. I. Design is based upon an inversion of the apparatus of FIG. 1.

FIG. 1 I is a transverse sectional view taken along line 55 of FIG. 10.

FIG. 12 is a transverse sectional view taken along line 6-6 of FIG. 10.

FIG. 13 is an exterior end view of the apparatus illus trated in FIG.10, taken along line 7-7.

FIG. 14 is a fragmentary longitudinal sectional view through anapparatus which is a multiple variation of the apparatus illustrated inFIG. 10.

FIG. 15 is an exterior end view of the apparatus illustrated in FIG. 14,taken along line l0l0.

FIG. 16 is an exterior upper view of the apparatus illustrated in FIG.14, including the terminal outlines of the entering and leaving fluidpassages.

FIG. 17 is a transverse sectional view taken along line 88 of FIG. 14.

FIG. 18 is a transverse sectional view taken along line 9 9 of FIG. 14.

FIG. 19 is an exterior end view of the apparatus illustrated in FIG. 14.

FIG. 20 is a fragmentary longitudinal sectional view of a receiver-sidesectional which provides means of axially adjusting the linear positionof its central annular intake-fluid nozzle member within thereceiver-side section.

FIG. 21 is a substantially exterior longitudinal view of the movablecompressed intake-fluid supply pipe and annular nozzle member shown inFIG. 20, together with its actuating linkage.

FIG. 22 is an exterior end view taken along line llll of FIG. 21.

FIG. 23 is a fragmentary longitudinal sectional view of a separator-sidesection which provides means of axially adjusting the linear position ofits central annular pre-heated intake fluid discharge member within theseparator-side section.

FIG. 24 is a substantially exterior longitudinal view of the movableannular pre-heated intake-fluid discharge member and discharge pipe asshown in FIG. 23, together with its actuating linkage.

FIG. 25 is an exterior end view taken along line 12-l2 of FIG. 24.

FIG. 26 is a fragmentary longitudinal sectional view of a heat exchangersimilar to the structure of FIG. I, which provides a slidable connectionin the mid-body of the heat exchanger and means of axially adjusting thelinear position of the receiver-side annular nozzlediffuser member withrespect to the separator-side annular exhaust-fluid discharge member.

FIG. 27 is a fragmentary longitudinal sectional view of a heat exchangersimilar to the structure of FIG. 10, which provides a slidableconnection in the mid-body of the heat exchanger and means of axiallyadjusting the linear position of the receiver-side intake-fluid nozzlemember with respect to the separator-side annular intake-fluid dischargemember.

FIG. 28 is an exterior frontal view of a heat exchanger apparatus whichmay find use in connection with contact heat exchange between the intakeair fluid and exhaust gas streams of a steam generator, furnace or othercombustion apparatus FIG. 29 is a fragmentary longitudinal sectionalview along line llll of the heat exchanger apparatus illustrated in FIG.28.

FIG. 30 is an exterior end view along line 12-l2 of the heat exchangerapparatus illustrated in FIG. 28.

FIG. 31 is a transverse sectional view along line l3l3 of the heatexchanger apparatus illustrated in FIG. 29.

FIG. 32 is a transverse sectional view along line l4l4 of the heatexchanger apparatus illustrated in FIG. 29.

FIG. 33 is a modification to the heat exchanger structure of FIG. 28showing a fragmentary elevation of the receiver-side section whereinpressurized intake fluids supplied by a constant-delivery fan areaccelerated within supply ductwork nozzle passageways exterior to theheat exchanger proper, and supplied as highvelocity intake fluids tofluid passageways of the receiver-side section.

FIG. 34 is a fragmentary longitudinal sectional view taken along linel515 of FIG. 33.

FIG. 35 is an exterior end view taken along line 16-16 of the heatexchanger apparatus illustrated in FIG. 33.

FIG. 36 is a modification to the heat exchanger structure of FIG. 33showing a side elevation of intake-fluid supply ductwork for thereceiver-side section through which high-velocity intake fluids aresupplied to fluid passageways of the receiver-side section from a rotaryfan located exterior to the heat exchanger proper.

FIG. 37 is an exterior end view taken along line l7l7 of the intakefluidsupply ductwork illustrated in FIG. 36.

FIG. 38 is a fragmentary sectional modification to the contact heatexchanger structure of FIG. 1 wherein an adjustable coniform flowdivider is centrally disposed adjacent the throat section ofintake-fluid discharge ductwork to regulate the flow of pre-heatedintake fluids through the heat exchanger.

FIG. 39 is a fragmenatary sectional modification to the contact heatexchanger structure of FIG. wherein an adjustable coniform flow divideris centrally disposed adjacent the throat section of intake-fluiddischarge ductwork to regulate the flow of pre-heated intake fluidsthrough the heat exchanger.

As indicated earlier herein the present invention involves a physicaland mechanical arrangement upon the flow processes of a gas turbinepower plant, or other similar processes and heat transfer systems,whereby thermal and kinetic energy may be exchanged in parallel flowbetween adjacent contacting fluid streams traveling at differentvelocities and having no physical or mechanical separation between them.More exactly, the invention involves an assemblage of ducting chambersections and opposted sub-sonic, sonic, or super-sonic nozzle-diffuserconfigurations and combinations which guide the expansion andcontraction of fluids at initially different thermodynamic energy stateswithin their several fluid passages to substantially equal pressurestates for the purpose of facilitating the transfer of thermal energybetween the several fluid streams by contacting interchange, followed bythe reseparation of the several fluid streams after the energy transferprocess between the has been completed.

The present invention also involves an assemblage of appropriateentrance and exit configurations to the various ducting chamber sectionsfor the purpose of controlling the physical state of the fluid streamswhich enter and leave the ducting chamber.

According to the teachings of the present invention, low-pressureturbine exhaust gases, acting as the heat source to intake fluidspassing through the apparatus enters the receiver-side section of theducting chamber and are guided to a minimum-velocity, maximumpressurestate by flowing through the interior sub-sonic diffuser passage of acombination nozzle-diffuser member affixed to the exhaust gas entrancepipe or duct within the receiver-side section of the ducting chamber. Asshown in the illustrative embodiment of the drawings, the exteriorsurface of this same nozzlediffuser member together with the interiorwalls of the receiver-side section comprise an annular nozzle which mayhave either a convergent or convergent-divergent configuration. Theboundaries of the receiver-side nozzle passage serve to guide theexpansion of compressed intakes air fluid to a high-velocity,low-pressure state. As the high-velocity intake heating fluid stream(air) and the low-velocity exhaust cooling fluid stream (combustedturbine exhaust gases) leave their respective sides of the adjacentnozzle and diffuser passages within the receiver-side ducting chambersection at substantially equal pressures, the contact interchange ofthermal and kinetic energy between the low-velocity exhaust coolingfluid and the high-velocity intake heating fluid will take place inturbulent flow over a characteristic length within the mixing section ofthe ducting chamber. After thermal expansion of the intake heating fluidstream and thermal contraction of the exhaust cooling fluid stream hastaken place over the characteristic length within the ducting chambermixing section, the combined adjacent fluid streams are again physicallydivided on passage into a separator-side section of the ducting chamber.The contracted exhaust cooling fluid now passes into convergent nozzlepassage for discharge to the atmosphere. The pre-heated intake heatingfluid stream (air) plus a small-scale mixture of entrained combustionproducts from the exhaust cooling fluid stream, still traveling at ahigh velocity, enters an annular fluid passage comprised of the interiorwalls of the separator-side section of the ducting chamber and to theouter walls of the convergent atmospheric exhaust nozzle member. Thepre-heated intake fluid stream then leaves the separator-side ductingchamber section and enters a diffuser passage of either the subsonic orsuper-sonic variety, from whence it enters the supply system leading tothe combustion chamber. The effect the apparatus of the invention (oftencalled a regenerator) is to decrease the amount of heat energy whichmust be supplied by the fuel within the combustion chamber to raise theintake fluid streams to the upper operating temperature, and thusimprove the thermal efiiciency of the entire gas turbine power plant.

After the high-velocity intake fluid and the lowvelocity exhaust fluidstreams leave their respective sides of the nozzle-diffuser member andassume intimate contact with each other, highly complex energy transferrelationships between the adjacent fluid streams will exist in theirannular interfacial mixing region. Turbulent flow conditions would existwithin the high-velocity intake fluid stream as it leaves the exit lipon the nozzle side of the nozzle-diffuser member. Either laminar,transitional or turbulent flow conditions may exist within thelow-velocity exhaust fluid stream as it leaves the exit lip on thediffuser side of the nozzlediffuser member. A violently turbulentannular mixing region at the interface of the adjacent fluid streamswould exist downstream of the nozzle-diffuser member due to the largedifference in velocity between the adjacent fluid streams. Thisturbulent annular mixing region is particularly favorable to the rapidtransfer of momentum from the high-velocity intake fluid stream to thelow-velocity exhaust fluid stream; and to the accelerated transfer ofthermal energy from the highertemperature exhaust fluid stream to thelowertemperature intake fluid stream.

The annular region of extreme turbulence induced by the violentinterchange of momentum between particles of the high-velocity andlow-velocity fluid streams is described as the region of contactinterchange. At the present time, the complex mechanism of energytransfer between the adjacent fluid streams is only partly understood bythose skilled in the art. it has been the general practice in the art todescribe flow condi' tions in a turbulent mixing region in terms of anaverage velocity plus a fluctuating, time-varying velocity component inthe direction of mean flow, together with a fluctuating, time-varyingvelocity component perpendicular to the direction of mean flow. Fromthis practice has grown theories of turbulent mixing length, concepts ofdynamic eddy viscosity for describing momentum interchange in turbulentflow, concepts of eddy diffusivity or eddy heat conductivity fordescribing the flow of thermal energy across turbulent mixing regions,and other concepts which attempt to scientifically explain mass andenergy transport between fluid regions in turbulent flow.

However, it is known from observation, experiment and empirical formulaethat highly turbulent mixing zones are extremely favorable foraccelerated transfer of thermal energy between adjacent fluid regions.

lt should be understood that the fundamental approach to the problem ofachieving contact interchange between fluid streams at substantiallydifferent thermodynamic energy states and pressures consists of thefollowing stages:

1. Conversion of intake fluid pressure energy to maximum kinetic energy2. Conversion of exhaust fluid kinetic energy to maximum effectivepressure energy 3. Bringing the intake and exhaust fluid streams intophysical contact at substantially equal pressures in parallel flow withrespect to each other within the confines of a closed plenum or ductingchamber. The object of this stage is to divide flow within the mixingsection of the ducting chamber into fluid laminae having greatlydifferent moments.

4. After the energy transfer between the contacting fluid streams issubstantially complete, the greatly different momenta of the fluidlaminae is utilized to effect a substantial physical separation of theintake and exhaust fluid streams within the separator'side section.

5. The separated fluid streams are then discharged from theseparator-side section of the ducting chamber.

Another teaching of the present invention involves an inversion of thedesign arrangements previously described, which attains similar effectsand advantages by means of somewhat different arrangements and relatedconfigurations. Low pressure turbine exhaust gases,

acting as heat source to compressed intake fluids (air) passing throughthe apparatus are guided to a minimum-velocity maximum-pressure state byflowing through an exterior sub-sonic diffuser passage communicatingwith the receiver-side section of the ducting chamber. The compressedintake fluids are routed into the interior nozzle passage of a centralnozzle member by means of a connecting intake fluid supply pipe thatpierces the endwall of the receiver-side section, and expanded withinthe nozzle passage to a high-velocity, low-pressure state. As shown inthe drawings, diffused turbine exhaust gases enter the ducting chamberand flow into an annular fluid passage bounded by the exterior walls ofthe central receiver-side nozzle member and the interior walls of thereceiver-side section. The central nozzle passage defined by theinterior walls of the receiver-side nozzle member may have either aconvergent or converge nt-divergent configuration. The adjacent fluidstreams leave their respective sides of the receiver-side nozzle memberat substantially equal pressures, and flow into the mixing section ofthe ducting chamber in intimate contact with each other. The contactinterchange process takes place as previously described within themixing section. The large difference in momenta between the intake andexhaust fluid stream is again used to effect separation within theseparatorside section of the ducting chamber. The greater inertia of thepre-heated intake fluid stream now carries it substantially past theleading edge of a converging discharge member into a central fluidpassage, to which is connected a discharge pipe piercing the confiningboundaries of the separator-side section and leading to processesdownstream of the invention. The cooled exhaust fluid streamsubstantially passes into an annular fluid passage bounded by theexterior walls of the separator-side discharge member and the interiorwalls of the separator-side section, from whence it is exhausted frm theapparatus of the inventron.

As stated earlier herein, it is among the objects of the presentinvention to provide a feasible means of achieving contact interchangewhich will accelerate transfer of thermal energy to conditionsapproaching thermal equilibrium between the exhaust and intake fluidstreams of a gas turbine, or other heat engine, heat source or thermalprocess. This objective is achieved by an initial large-scale conversionof intake fluid pressure energy to kinetic energy, which in tum-aids thees tablishment of a highly turbulent mixing region between the adjacentfluid streams within the ducting chamber mixing section. It is thisviolent turbulence, largely induced by the high-velocity intake fluidstream, which will accelerate the large scale transfer of thermal energyfrom the hot exhaust fluid stream to the relatively cool intake fluidstream. Due to the large velocity difference between the adjacent fluidstreams,

it is expected that both the mixing and characteristic lengths overwhich energy transfer is substantially complete will be of modestdimension.

If the contact regenerators described were part of a gas turbine powerplant which combusted ordinary refinery fuels, particularly of the heavyresidual variety, the concentration of combustion products within theworking fluid branch serving the gas turbine would slowly increase. Thisincrease in combustion products concentration within the working fluidbranch serving the gas turbine would occur because combustion productsentrained in the region of contact interchange would be partiallyrecirculated through the gas turbine rather than being dischargeddirectly to the atmosphere. The rising combustion products concentrationin the working fluid stream serving the turbine would result in thebuild-up of heavy deposits on the blade surfaces of the gas-generatorturbine and upon surfaces within the combustion chamber, since solidcombustion products would tend to adhere to surfaces in the hotter partsof the thermal process as the solids products melting points areapproached. The present invention results in several ways of avoidingthis problem, such as:

l. A purge control method of temporarily increasing atmospheric exhaustnozzle throat area which will evacuate excessive concentration ofcombustion products from the working fluid branch serving the gasturbine.

II. A segregation method of arranging gas turbine power plant flowprocesses which is schematically presented in FIG. 8. This arrangementdiffers from the more conventional schematic flow process of FIG. 7 inthat the regenerator is the sole direct heat source for both thegas-generator turbine and free turbine, and that major quantities ofheat energy are added to the exhaust fluid stream by a downstreamcombustor after expansion of the working fluid has taken place withinthe turbines. In this method, all but a small percentage of the productsof combustion are discharged directly to the atmo sphere without passingthrough the turbines.

It is expected that method I, referred to immediately hereinbefore, or acombination of methods I and ll will entirely relieve the solid productsdeposit problems as it occurs in ordinary practice.

Still another teaching of the present invention involves the arrangementof a plurality of central receiver-side nozzle members within thereceiver-side section of an integral plenum or ducting chamber opposinga plurality of converging discharge members within the separator-sidesection. This multiple version would be useful for effecting contactinterchange between the intake and exhaust fluid streams of power plantapparatus involving very large flow rates. As shown in the drawings, theplurality of central receiver-side nozzle members is supplied from acommon compressed intake fluid receiver through a plurality of supplypipes which pierce the confining boundaries of the receiverside section.Hot low-pressure exhaust gases, acting as the heat source to thecompressed intake fluids passing through the apparatus, enter the fluidpassage defined by the exterior surfaces of the plurality ofreceiver-side nozzle members and their supply pipes together with theinterior walls of the receiver-side section of the ducting chamber. Theexpansion of the compressed in' take fluid streams within thereceiver-side nozzle passages to a high-velocity low-pressure statetakes piace as previously described. The contact interchange processtakes place along the plurality of interfacial mixing regions within themixing section, and the larger inertias of the pre-heated intake fluidstreams are again used to separate the intake and exhaust fluid streamswithin the separatonside section. The pre-heated intake fluid streamsare substantially diverted into the plurality of opposed and convergingdischarge members, which have connecting pipes that pierce the confining boundaries of the separator-side section. The

cooled exhaust fluid stream is substantially diverted into the fluidpassage defined by the exterior surfaces of the plurality of convergingseparator-side discharge members and their supply pipes together withthe interior walls of the separator-side section. The pre-heated intakefluid streams are thence routed to processes downstream of theinvention, while the cooled exhaust fluid stream is exhausted from theducting chamber.

Thermodynamic properties of intake fluids (air) entering regenerativeatmospheric gas turbine power plants would vary in accordance withambient atmospheric conditions. This continuing change in thethermodynamic properties of air intake fluids would be reflected asminor variations in the linear dimension of characteristic length overwhich contact interchange takes place within the regenerative apparatusof the invention. Effective local adjustments between the rcceiver-sideannular nozzle member and the separatorside annular discharge member tothe optimum charao teristic length becomes necessary to limit formationoof normal shock waves in supersonic flow across the leading edge of theannular discharge member of the separator-side section.

Yet another teaching of the present invention involves means ofadjusting linear position of the central annular nozzle member withinthe receiver-side section with respect to the leading edge of itscorresponding opposite central annular discharge member of theseparator-side section. This arrangement permits local adjustments tothe optimum characteristic length di mension within the mixing sectionof the heat exchanger in accordance with variable atmosphericconditions. The linear position of the central annular discharge memberwithin the separatorside section may be alternately adjusted withrespect to the trailing edge of its corresponding opposite centralannular nozzle member of the receiver-side section to provide equivalentvariable adjustment to optimum characteristic length. The methoddescribed for effecting local adjustment to the optimum characteristiclength dimension may be applied to either the central annular nozzlemembers of the receiver-side section or the central an nular dischargemembers of the separator-side section in any of the heat exchangersdisclosed in connection with either of FIGS. 1, 10 or 14.

Certain types of gas turbines exhausting to atmospheric pressures whichdo not produce solid products in their combustion process, such asalcoholfired tur bines, will not require periodic purging ofrecirculated and entrained combustion products from the working fluidbranch serving the gas turbine. Such gas turbine power plants willrequire a method of adjusting exhaust nozzle throat area so that exhaustnozzle pressure will not exceed atmospheric pressure. The operatinglinkage of FIGS. 5 and 6 may be actuated by a handoperated power screwas schematically presented in the sectional diagram of FIG. 9. in thisvariation, the movable fulcrum pin of the lever together with theoperation of the threaded force rod combine to compose an adjustablepositioning system which flexibly holds the conical throat piece in adesired position with respect to the atmospheric exhaust nozzle throatso as to effec tively control the cross sectional flow area of theexhaust nozzle.

Heat energy may also be admntagcously transferred between the intakeair-fluid and exhaust gas streams of a steam generator, furnace or othersimilar combustion apparatus by means of the contact-type heat exchangerillustrated in FIGS. 28, 29, 30, 3] and 32. In this apparatus,pressurized intake air is supplied by a forced draft fan and expanded insub-sonic nozzle passageways of the heat exchanger. The high-velocityintake air-fluid stream and the hot low-velocity exhaust gas stream areeach divided into several adjacent alternately contacting fluid streamsin parallel flow with respect to each other. Following the contactinterchange process, the heated intake fluid streams and the cooledexhaust gas streams are substantially separated from each other. Theapparatus shown in H68. 28, 29, 30, 3l and 32 would be described in theart as a contacttype air preheater for a steam generator or furnace.

Referring more particularly to the accompanying drawings, FIG. Ispecifically illustrates a longitudinal section of the invention in theform of an atmospheric gas turbine regenerator which is part of theapparatus of an atmospheric gas turbine power plant. ln this atmosphericgas turbine regenerator compressed air enters intake fluid supply pipe 8having a socket flange 9 secured thereto. From this intake fluid supplypipe 8 the compressed air flows into optional sub-sonic diffuser section11 which is fitted with an entrance flange l and an exit flange 12. Thecompressed intake airfluid then passes through an entrance flange l3 andinto receiver-side ducting chamber section 14. As shown, this receiverside ducting chamber section 14 is provided with an exit flange 15 whichis angularly disposed with respect to its entrance flange 13.

The receiver-side ducting chamber section 14 receives hot sub-sonicexhaust gases from the exhaust fluid supply pipe 16 of the turbine orcombustor which is centrally disposed therein, extending through theadjacent end wall as shown.

Within the receiver-side ducting chamber section 14, and concentricallydisposed with respect thereto is an annular nozzle-diffuser member 17which is connected to exhaust fluid supply pipe 16 and stabilized byintermediately disposed bracket or spider member 18. The inner surfaceof the annular nozzle-diffuser member 17 is outwardly flared and definesa diverging sub-sonic diffuser passage 22, wherein the hot exhaust fluidis guided to a thermodynamic energy state of maximum pressure andminimum velocity.

The space between the outer surface of the annular nozzle-diffusermember 17 and the interior of the receiver-side ducting chamber section14 defines an annular super-sonic nozzle composed of convergent subsonicfluid passage 19, annular sonic fluid passage 20, and divergent annularsuper-sonic fluid passage 21. The purpose of the annular super-sonicnozzle composed of the successive fluid passages 19, 20 and 21 is toguide the expansion of the compressed intake fluid stream until thepressure at the exit lip of the annular super-sonic nozzle issubstantially equal to the pressure on the inner side of thenozzle-diffuser member 17, the said exit lip terminating at the end ofthe subsonic diffuser passage 22.

The expanded intake fluid stream leaves the exit lip of the fluidpassage 21 traveling at super-sonic speed, while the compressed exhaustfluid stream leaves the exit lip of the diffuser passage 22 traveling ata low subsonic speed. As the adjacent high-velocity intake fluid streamand the low-velocity exhaust fluid stream leave the nozzle diffusermember 17 on their respective sides of the exit lip, a violent contactinterchange of kinetic .snamnmhhanr.kum-isw... nu-A and thermal energytakes place with turbulent mixing along the interface between theadjacent fluid streams.

The exit flange 15 of the receiver-side section 14 is connected to theentrance flange 23 of a cylindrical mixing section 24, the latter beingalso provided with an exit flange 25.

The aforementioned contact interchange of kinetic and thermal energybetween the adjacent fluid streams largely takes place within theboundaries of the mixing section 24. The outer intake heating fluidstream expands within the annular fluid passage region 26 of the mixingsection as the thermal energy flows across the annular region of contactinterchange, while the inner exhaust cooling fluid stream contractswithin the fluid passage region 27 of the mixing section as thermalenergy is transferred from the exhaust fluid stream.

The process of contact interchange is substantially complete as theintimately associated fluids leave the outlet of the mixing section 24.

The exit flange 25 of the mixing section 24 is connected to the entranceflange 28 of the separator-side section 29, the latter being alsoprovided with an exit flange 30.

After the intimately associated fluids leave the mixing section 24, theypass into the separator-side section 29 of the ducting chamber and thefluid streams are again divided. Centrally disposed within theseparatorside section 29 there is a frusto-conical atmospheric exhaustnozzle member 3], the convergent end of which terminates in acylindrical throat section 34 which extends through and projects fromthe adjacent endwall of the separator-side section. Adjacent its largerend the frusto-conical atmospheric exhaust noule member 31 is stabilizedby bracket or spider members 32.

From the foregoing it will be perceived that the inner exhaust fluidstream enters the converging nozzle passage 33 and exits at atmosphericpressure from the cylindrical throat 34 at the convergent end of thefrustoconical exhaust nozzle member 31. The outer, annular pre-heatedintake fluid stream passes into the diverging passage formed by theinner walls of separator-side ducting chamber section 29 and the outerwalls of the frusto-conical exhaust nozzle member 31.

Referring to the right-hand side of FIG. 1, a conical divider or throatpiece 35 is disposed to extend axially into the exhaust noule throat 34,the same being mounted on the end of a slidable control rod 37 andsecured by a lock nut 36.

The slidable control rod 37 is mounted to extend through an annularcollar 38, the latter being provided with a bushing 39.

This annular collar 38 is supported by a bracket or spider 40 which willbe referred to hereinafter.

To the outer end of the separator-side section 29 of the ducting chamberthere is secured the annular end flange 41 of the exhaust duct 42, theother end of said exhaust duct being provided with an exterior boss 43having a bushing 44 extending therethrough.

The bracket or spider 40 which supports the slidable control rod 37 issecured to the interior walls of the exhaust duct 42 and the outer endof said rocl extends through and projects from the bushing 44 in theexterior boss 43 on the outer end of the exhaust duct 42.

According to the foregoing construction and arrangement the concialdivider or throat piece 35 may be retracted to purge control position35' which is clear of the throat 34 of the atmospheric exhaust nozzle 31when the slidable control rod 37 is caused to retract along thelongitudinal axis of the ducting chamber by variable force F (seeright-hand end of FIG. 1). The temporary increase in cross-sectionalflow area occasioned by the retraction of the conical throat piece 35(to purge control position 35') permits an increased discharge of cooledexhaust gases to the atmosphere through the exhaust duct exit 46 and aconsequent purging of the entrained combustion products which may berecirculated within fluid system branches downstream of the apparatus ofthe invention, as will be understood by those skilled in the art.

As also shown in FIG. 1, the pre-heated intake fluid stream passesthrough the exit flange 30 of the separa tor-side section 29 and throughthe entrance flange 47 of the aforementioned optional diffuser section48, the latter being also provided with an exit flange 49. While flowconditions may be either sub-sonic or super-sonic at this pointdepending upon the design parameters chosen for a particularinstallation, flow velocity is assumed to be supersonic for the purposesof the present illustrative disclosure.

The optional diffuser section 48 is shown as being of invertedfrusto-conical shape and its interior walls 50 provide a convergentsuper-sonic diffuser passage 51 and a lower cylindrical sonic diffuserthroat section 52.

Exit flange 49 of the converging super-sonic diffuser member 48 isconnected to the entrance socket flange 53 of intake fluid dischargepipe 54.

The pressure drop resulting in moving over the relatively short lengthof the interior walls 55 of the combustor supply pipe 54 will besufficient to insure a slightly sub-sonic velocity; accordingly adiverging diffuser section might be added to the combustor supply pipe54 downstream with respect to the entrance socket flange 53 should afurther reduction of the preheated intake fluid stream velocity bedesired before entering a combustion chamber.

An additional variation for regulating the flow of intake fluids throughthe contact heat exchanger structure of FIG. 1 is disclosed in theillustrative embodiment of FIG. 38. In FIG. 38 exit flange 49 ofoptional super-sonic diffuser section 48 (FIG. 1) connects to socketflange 311, the same housing annular sonic throat section 312. Annularsonic throat section 312 is secured by welding or other suitable meansto annular sub-sonic diffuser section 313, which is similarly secured tointake-fluid discharge conduit 314. Coniform flow divider or throatpiece 317 is suitably attached to the end of slidable control rod 318and disposed centrally of annular sonic throat section 312 and annulardiffuser section 313. Slidable control rod 318 extends through bushing321 and annular collar 320 of spider assembly 319 (attached to dischargeconduit 314), and through bushing 322 and exterior duct boss 315.Variable force F acting on slidable control rod 318 as shown may adjustconiform flow divider or throat piece 317 to any position along thecontrol axis with respect to annular throat section 312 or diffusersection 313. Throat control assembly 317-318 may be actuated by theadjustable pneumatic control apparatus of FIGS. and 6, or by othersuitable means.

Intake-fluid discharge throat control assembly 317-318 inclusive andexhaust-fluid throat control as sembly 35-37 may be joinly operated bytheir respective control apparatuses to dampen pressure fluctuationswithin the contact heat exchanger, or to regulate the contactinterchange process.

The schematic diagram of FIG. 7 represents the application of theinvention to the thermodynamic processes of an atmospheric gas turbinepower plant. Atmospheric air at thermodynamic energy state 56 enters acompressor 57 (driven by the shaft member 66 of the gas-generatorturbine 64) where it is compressed to thermodynamic energy state 58. Thecompressed intake air then enters the regenerative apparatus of theinvention (59) where it is pre-heated by contact interchange in parallelflow with the hot exhaust gases of free turbine 67. The pre-heatedintake fluid stream leaves the regenerative apparatus of the invention(59) at thermodynamic energy state 60. The pre-heated intake fluidstream then enters combustion chamber 61 where fuel is injected atthermodynamic energy state 62, and combustion then proceeds within thecombustor. The high-temperature combusted fluid stream leaves combustionchamber 61 at thermodynamic energy state 63 and is expanded ingas-generator turbine 64 (having a shaft member 66 which drives thecompressor S7). The combusted fluid stream leaves the gasgeneratorturbine 64 at thermosdynamic energy state 65, and is further expanded infree turbine 67 having a shaft member 70 which drives an alternator 71or other work-absorbing device. The combusted fluid leaves the freeturbine 67 at thermodynamic energy state 68, and enters theaforementioned regenerative apparatus of the invention (59) in aparallel flow direction with the intake fluid stream traveling betweenthermodynamic energy states 58 and 60.

Within the regenerative apparatus of the invention (59) the combustedexhaust fluid stream is cooled by contact interchange in parallel flowwith the intake fluid stream, and discharged to atmosphere atthermodynamic energy state 69.

The schematic diagram of FIG. 8 represents a novel application of theapparatus of the invention to the thermodynamic processes of anatmospheric gas turbine power plant. wherein the blading of the turbinesis substantially protected from fouling by deposit of the products ofcombustion. All of the initial heating of intake air-fluid isaccomplished within the regenerative apparatus of the invention (59) andthe combustion process is entirely carried out in the free turbineexhaust fluid stream. .Save for a small amount of entrained combustionproducts within the pre-heated intake fluid stream, no combustionproducts will pass directly through the gas-generator turbine 64 or thefree turbine 67. The fouling of blading surfaces within the turbines bydeposit of the products of combustion is thus bypassed almost entirelyby the method of segregation.

Referring still to FIG. 8, atmospheric air at thermodynamic energy state56 enters compressor 57 (driven by the shaft member 66 of thegas-generator turbine 64) where it is compressed to thermodynamic energystate 95. The compressed intake air stream then enters the regenerativeapparatus of the invention (59) where it is pre-heated by contactinterchange in parallel flow with the high-temperature exhaust gasesfrom combustion chamber 61. The pre-heated intake fluid stream leavesthe regenerative apparatus of the invention (59) at thermodynamic energystate 96, and is then expanded in gas-generator turbine 64 (drivingcompressor 57, etc.). The pre-heated fluid stream leaves gasgeneratorturbine 64 at thermodynamic energy state 97, and is then furtherexpanded in free turbine 67 (having shaft member 70 which drivesalternator 71 or other work-absorbing device). The expanded fluid streamleaves free turbine 67 at thermodynamic energy state 98, and enters thecombustion chamber 61. Within the combustion chamber 61 fuel is injectedat thermodynamic energy state 99, and the combustion process proceedstherewithin. The combusted hightemperature exhaust fluid stream leavesthe combustion chamber 61 at thermodynamic energy state 100, and entersthe regenerative apparatus of the invention (59) in parallel flow withthe intake fluid stream traveling between thermodynamic energy states 95and 96. Within the regenerative apparatus of the invention (59) thecombusted exhaust fluid stream is cooled by contact interchange inparallel flow with the intake fluid stream, and then discharged toatmosphere at thermodynamic energy state 101.

FIG. 5 is a schematic diagram partially in section, of a piston-actuatedcontrol system for carrying out the purging operation on a cyclicalbasis. In this figure the pneumatic control system is illustrated whenit is approaching the normal operating position, wherein the conicalflow divider or throat piece 35 would be nearly disposed in the correctposition with respect to exhaust nozzle throat 34 of the atmosphericexhaust nozzle member 31. As shown, the slidable control rod 37 carriesa yoke fitting 72 which houses a yoke pin 73. A lever 74 is providedwith a guide slot 75 for receiving the yoke pin 73; and in this mannerthe motion of the lever 74 is transmitted to the slidable control rod37.

The lever 74 pivots about an adjustable fulcrum pin 76 and has a guideslot 77 within which a yoke pin 78 is slidably disposed. This yoke 78 ishoused in a yoke fitting 79 and the adjustable fulcrum pin 76 is housedby a traveler member 80 which is threaded onto a power screw member 81.This power screw member 81 is housed in machine-frame socket member 82by a suitable sleeve-type bushing, and in machine-frame bearing member83 by sleeve-type bushing and thrust collars. A handwheel 84 rotatesthis power screw member 81 to cause the traveler member 80 to advance orretract along the threaded shaft, thus adjusting the linear position ofthe fulcrum pin 76.

The yoke fitting 79 is secured to the piston rod 85 of a pneumaticdouble-acting piston 86 which is disposed in a cylinder 87, and in thismanner the movement of said piston is transmitted to the slidablecontrol rod 37.

The numerals 88 and 89 designate pipe branch members which are connectedto the upper and lower lefthand orifices of a four-way valve 90.

A pneumatic supply pipe 91 is connected to the upper right-hand orificeof the four-way valve 90, and an exhaust pipe 92 is connected to thelower right-hand orifice thereof.

A solenoid 93, forming part of an electrical pilot circuit 94, may beutilized to control the operation of the double-acting piston 86 in thecylinder 87. When the solenoid 93 is de-energized, compressed air willflow from the pneumatic supply pipe 91 into the upper righthand orificeof the four-way valve 90 into the pipe branch member 88 with thedirection of flow indicated by the arrows. in this manner the compressedair enters the cylinder 87 to act upon the rod face of piston 86,causing the piston to move to the right as viewed in the drawings. Thismovement of the piston 86 exhausts low-pressure air from the cylinder 87into the pipe branch member 89, which communicates with the lowerleft-hand orifice of the four-way valve 90. Exhausted air then flowsthrough the four-way valve into the exhaust pipe 92 (which communicateswith the lower right-hand orifice of the four-way valve), from whencethe exhaust air leaves the pneumatic control system.

it will be understood that the installation of an additional cross-overvalve connection between the pneumatic supply pipe 91 and the exhaustpipe system 92 downstream of the aforementioned four-way valve plus astop valve fitting within the exhaust pipe 92 system downstream of saidcrossover valve connection will permit the pneumatic control system tohold the piston 86 in any desired operating position within the cylinder87.

FIG. 6 is a schematic diagram, partly in section, of the pneumatic purgecontrol system, wherein the apparatus of the control system is shown asnearing the retracted purge operating position. The movement of thepiston 86 within the cylinder 87 is now disclosed as opposite to thatillustrated in FIG. 5; and the control system linkage has retracted theconical throat piece 35 form the exhaust nozzle throat 34.

According to FIG. 6, the solenoid 93 has been energized by theelectrical pilot circuit 94, thereby actuating the four-way valve 90 tocross-route the compressed air supply from the pneumatic supply pipe 91to the pipe branch member 89. Thus, the compressed air enters thecylinder 87 to act upon the head face of the piston 86, causing thepiston to move within the cylinder 87 to the left as illustrated. Thismovement of the piston 86 exhausts low-pressure air from the cylinder 87into the pipe branch member 88. The exhausted low-pressure air is thencross-routed from the pipe branch member 88 to the pneumatic exhaustpipe 92 by the four-way valve 90, from whence the exhaust air leaves thepneumatic control system.

In this connection, it will be understood that the installation of anadditional crossover valve connection between the pneumatic supply pipe91 and the pneumatic exhaust pipe 92, together with a stop valve fittingwithin the exhaust pipe system 92 downstream of the additional crossovervalve connection will permit the pneumatic control system to hold thepiston 86 in any desired operating position within the cylinder 87, whensaid stop and crossover valves are jointly operated.

FIG. 9 is a schematic diagram of the throat piece operating linkage ofFlGS. 5 and 6 (ie adjustable lever type) as actuated by a hand operatedpower screw. This form of throatpiece control apparatus may be utilizedto insure that exhaust nozzle discharge and throat pressures areadjusted to the optimum conditions consistent with ambient atmosphericconditions, simply by adjusting the position of the conical throat piece35 with respect to the exhaust nozzle throat 34. According to thisembodiment there is no provision for a cyclic retraction of the conicalthroat piece 35 form the exhaust nozzle throat 34 as occurs in the purgecontrol apparatus illustrated in FIGS. 5 and 6, since the handoperatedtype is for use in connection with the regener' ative apparatus of gasturbine power plants exhausting to atmospheric pressures and which donot produce solid combustion products in their combustion process.

Rotation of the handwheel imparts similar movement to the power screwshaft member 103 within the threaded machine-frame housing 104, causingthe power screw shaft member to advance or retract with respect to thesaid machine-frame housing. The end of the power screw shaft member 103opposite to that carrying the handwheel 105 is fitted with a tuned andnecked end which may rotate freely within the socket member 102 which isaffixed to the yoke fitting 79. The power screw shaft member 103 may beadditionally stablized by a sleeve-type bushing housed in an additionalmachine-frame bearing member, or by other suitable means. The lever-typelinkage of P16. 9 functions similarly to the lever-type linkage of FIGS.and 6 when the double-acting piston 86 is held in a fixed position,wherein the position of the conical throat piece 35 is adjustable byboth the actuating power screw shaft member 103 and the fulcrum screwshaft member 81 acting separately or in conjunction with each other.

FIG. specifically illustrates a longitudinal section of the invention inthe form of an atmospheric gas turbine regenerator whose designrepresents an inversion of the illustrative embodiment of FIG. 1. Hotlowpressure turbine exhaust gases enter exhaust fluid sup ply pipe 106,which is fitted with exit flange 107. Exit flange 107 of exhaust fluidsupply pipe 106 is connected to entrance flange 108 of diffuser member109, the latter also being provided with exit flange 110. The hot-lowpressure exhaust gases flow from supply pipe 106 into an interiordiffuser passage of diffuser member 109 defined by interior walls 111,where they are guided to a minimum-velocity, maximum pressure state.Exit flange 110 of diffuser member 109 is connected to entrance flange112 of receiver-side section 113, the latter also being provided withangularly disposed exit flange 114. The compressed exhaust gases passfrom diffuser member 109 into receiver-side section 113 through itsentrance flange 112.

Receiver-side ducting chamber section 113 receives compressed intakefluid (air) from intake fluid supply pipe 115, which is centrallydisposed and extends through the adjacent endwall as shown.

Within receiver-side ducting chamber section 113 and concentricallydisposed with respect thereto is an annular nozzle member 116, which isconnected to intake fluid supply pipe 115 and stabilized byintermediately disposed bracket or spider members 117. The inner surfaceof receiver-side nozzle member 116 defines the boundaries of aconvergent-divergent nozzle composed of sub-sonic nozzle passage 1 18,sonic nozzle passage 119 and super-sonic nozzle passage 120. Within thereceiver-side nozzle passage 118, 119 and 120, the compressed intakefluid stream is guided and expanded to a high-velocity, low-pressurestate. The space between the outer surface of annular nozzle member 116and the interior walls of receiver-side section 113 composes an annularfluid passage 121, which is in turn supplied with compressed exhaustgases from diffuser member 109. The purpose of the super-sonic nozlecomposed of successive fluid passages 118, 119 and 120 is to guide theexpansion of the compressed intake fluid stream until the pressure atthe exit lip of the super-sonic nozzle is substantially equal to thepressure of the hot exhaust gases on the outer side of annular nozzlemember 116 in exhaust fluid passage 121.

The expanded intake fluid stream leaves the exit lip of fluid passage120 traveling at super-sonic speed, while the compressed exhaust fluidstream leaves annular exhaust fluid passage 121 traveling at a lowsubsonic speed. As the adjacent high-velocity intake fluid stream andthe low-velocity exhaust fluid stream leave annular nozzle member 116 ontheir respective sides of the exit lip, a violent contact interchange ofkinetic and thermal energy takes place with turbulent mixing along theannular interface between the adjacent fluid streams.

The adjacent intake and exhaust fluid streams leave receiver-sidesection 113 and pass into mixing section 123, which is fitted withentrance flange 122 and exit flange 124. Exit flange 114 ofreceiver-side section 113 is connected to entrance flange 122 of mixingsection 123.

The previously mentioned contact interchange of thermal and kineticenergy between the adjacent fluid streams largely takes place within theboundaries of mixing section 123. The inner high-velocity intake heatingfluid stream expands within the inner fluid passage region 126 of themixing section as thermal energy flows across the annular interfacialregion of contact interchange, while the outer exhaust cooling fluidstream contracts within annular fluid passage region of the mixingsection as thermal energy is transferred from the exhaust fluid stream.The process of contact interchange is substantially complete as theintimately associated fluid streams leave the outlet of mixing section123.

Exit flange 124 of mixing section 123 is connected to entrance flange127 of separator-side section 128, the latter being provided withangularly disposed exit flange 129.

After the intimately associated fluid stream leave the mixing section123, they pass into separator-side section 128 of the ducting chamberand the fluid streams are again divided. Centrally disposed withinseparatorside section 128 there is a frusto-conical discharge member130, the convergent end of which is connected to discharge pipe member131, which in turn pierces the endwall of separator-side section 128.The substantially greater inertia of the pre-heated intake fluid streamcarries it past the entrance lip of separator-side discharge member 130into convergent fluid passage 132 defined by the interior walls of theaforesaid discharge member. Adjacent its larger end. the convergentdischarge member 130 is stabilized by intermediately disposed bracket orspider members 133. The pre-heated intake fluid stream is dischargedfrom discharge fluid passage 132 through discharge pipe 131 from theducting chamber to processes downstream of the invention.

After passing the entrance lip of separator-side discharge member 130,the cooled exhaust fluid stream enters the converging annular exhaustfluid passage 134, defined by the exterior surfaces of the convergentdischarge member 130 and its connecting discharge pipe 131 together withthe converging interior walls of the separator-side section. It shouldbe particularly noted that the walls of separator-side section 128converge from the inlet at the entrance flange 127 to the outlet at theangularly disposed exit flange 129.

Exit flange 129 of separator-side section 128 is connected to entranceflange 142 of atmospheric exhaust duct 144, from which the cooledexhaust fluid is finally exhausted to the atmosphere.

The reduction in cross sectional exhaust fluid flow area within theseparator-side section composes an effective convergent exhaust nozzlewhich terminates in

1. A non-reversing single-pass fluid-to-fluid contact heat exchangeradapted to receive and exchange energy between a plurality of fluidstreams at different thermodynamic energy states in parallel flow withrespect to each other; said contact heat exchanger comprising asubstantially closed plenum or ducting chamber defined by side andconfining walls and providing receiver-side, mixing and separator-sidesections, said mixing section disposed in said ducting chamber betweenthe receiverside and separator-side sections thereof; intake andexhaustfluid passageways disposed within both the aforesaid receiversideand separator-side ducting chamber sections, the boundaries of the saidintake and exhaust-fluid passageways being defined by the interior wallsof said ducting chamber and the surfaces of annular internal fluid flowcontrol members of substantially lesser cross section than aid disposedcentrally of both their respective receiver-side and separator -sidesections; an intakefluid supply pipe(s) or duct(s) in communication withthe receiver-side intake-fluid passageway(s), and supplying intakefluids thereto; and exhaust-fluid supply pipe(s) or ducts(s) incommunication with the receiver-side exhaust-fluid passageway(s) andsupplying hot, low-pressure exhaust fluids thereto; an intake-fluiddischarge pipe(s) or duct(s) in communication with the separator-sideintake fluid passageway(s) and receiving heated intake fluids therefrom;and an exhaust-fluid discharge pipe(s) or duct(s) in communication withthe separator-side exhaust-fluid passageway(s) and receiving cooledexhaust fluids therefrom; whereby particles of the aforesaidintake-fluid and exhaust-fluid streams aare brought into physicalcontact with each other within said mixing section at substantiallyequal pressures while possessing substantially unequal and parallelvelocity vectors so as to facilitate the contact interchange of thermaland kinetic energy therebetween, followed by a reseparation of theaforesaid intake and exhaust-fluid streams within the separator-sidesection of said contact heat exchanger after the contact interchangeprocess has been substantially completed.
 2. A non-reversing single-passfluid-to-fluid contact heat exchanger adapted to receive and exchangeenergy between a plurality of fluid streams at different thermodynamicenergy states in parallel flow with respect to each other; said contactheat exchanger comprising a substantially closed plenum or ductingchamber definEd by side and confining walls and providing receiver-side,mixing and separator-side sections, said mixing section disposed in saidducting chamber between the receiver-side and separator-side sectionsthereof; an annular nozzle member of substantially lesser cross sectionthan and disposed centrally of said receiver-side section whose outersurfaces and the walls of the receiver-side section define an annularintake-fluid nozzle passageway discharging to said mixing section, andwhose inner sufaces defines an exhaust-fluid passageway discharging tosaid mixing section; an intake-fluid supply pipe or duct incommunication with the annular enveloping intake-fluid nozzle passagewayof the receiver-side section and supplying compressed intake fluidsthereto; an exhaust-fluid supply pipe or duct in communication with thecentral exhaust-fluid passageway of the receiver-side section andsupplying hot, low-pressure exhaust fluids thereto; whereby particles ofthe aforesaid intake-fluid and exhaust-fluid streams are brought intophysical contact with each other within said mixing section atsubstantially equal pressures while possessing substantially unequal andparallel and velocity vectors so as to facilitate the contactinterchange of thermal and kinetic energy therebetween; an annulardischarge member of substantially lesser cross section than and disposedcentrally of said separator-side section whose outer surfaces and thewalls of the separator-side section define an annular intake-fluiddischarge passageway receiving heated intake fluids from said mixingsection, and whose inner surfaces define an exhaust-fluid dischargepassageway receiving cooled exhaust fluids from said mixing section,whereby the leading edge of said annular discharge member serves as aflow divider to separate the intake-fluid and exhaust-fluid streams fromeach other after the contact interchange process as flows proceeds fromthe mixing section into said separator-side section; an intake-fluiddischarge pipe or duct in communication with the annular envelopingintake-fluid discharge passageway of the separator-side section andreceiving heated intake fluid therefrom; and an exhaust-fluid dischargepipe or duct in communication with the central exhaust-fluid dischargepassageway of the separator-side section whereby cooled exhaust fluidsmay be discharged from the apparatus of the invention.
 3. Thenon-reversing single-pass fluid-to-fluid contact heat exchanger of claim2 wherein the annular nozzle member is disposed coaxially with thereceiver-side section along the flow axis thereof.
 4. The non-reversingsingle-pass fluid-to-fluid contact heat exchanger of claim 2 wherein theannular discharge member is disposed coaxially with the separator-sidesection along the flow axis thereof.
 5. The non-reversing single-passfluid-to-fluid contact heat exchanger of claim 2 wherein a coniform flowdivider is disposed axially of an exhaust-fluid discharge aperturesupplied by the said central exhaust-fluid discharge passageway of theseparator-side section and directed against the discharge of cooledexhaust fluids therefrom, and means for axially advancing and retractingthe said coniform flow divider with respect to the said exhaust-fluiddischarge aperture.
 6. A non-reversing single-pass fluid-to-fluidcontact heat exchanger adapted to receive and exchange energy between aplurality of fluid streams at different theremodynamic energy states inparallel flow with respect to each other; said contact heat exchangercomprising a substantially closed plenum or ducting chamber defined byside and confining walls and providing receiver-side, mixing andsepartor-side sections, said mixing section disposed in said ductingchamber between the receiver-side and separator-side sections thereof;an annular nozzle member of substantially lesser cross section than anddisposed centrally of said receiver-side section whose inner surfacesdefine a central intake-fluid nozzle passageway discharging to saidmixing Section, and whose outer surfaces and the walls of thereceiver-side section define an annular exhaust-fluid passagewaydischarging to said mixing section; an intake-fluid supply pipe or ductin communication with the central intake-fluid nozzle passageway of thereceiver-side section and supplying compressed intake fluids thereto; anexhaust-fluid supply pipe or duct in communication with the annularenveloping exhaust-fluid passageway of the receiver-side section andsupplying hot, low-pressure exhaust fluids thereto; whereby particles ofthe aforesaid intake-fluid and exhaust-fluid streams are brought intophysical contact with each other within said mixing section atsubstantially equal pressures while possessing substantially unequal andparallel and velocity vectors so as to facilitate the contactinterchange of thermal and kinetic energy therebetween; an annulardischarge member of substantially lesser cross section than and disposedcentrally of said separator-side section whose inner surfaces define acentral intake-fluid discharge passageway receiving heated intake fluidsfrom said mixing section, and whose outer surfaces and the walls of theseparator-side section define an annular exhaust-fluid dischargepassageway receiving cooled exhaust fluids from said mixing section,whereby the leading edge of said annular discharge member serves as aflow divider to separate the intake-fluid and exhaust-fluid streams fromeach other after the contact interchange process as flow proceeds fromthe mixing section into said separator-side section; an intake-fluiddischarge pipe or duct in communication with the central intake-fluiddischarge passageway of the separator-side section and receiving heatedintake fluids therefrom; and an exhaust-fluid discharge pipe or duct incommunication with the annular enveloping exhaust-fluid dischargepassageway of the separator-side section whereby cooled exhaust fluidsmay be discharged from the apparatus of the invention.
 7. Thenon-reversing single-pass fluid-to-fluid contact heat exchanger of claim6 wherein the annular nozzle member is disposed coaxially with thereceiver-side section along the flow axis thereof.
 8. The non-reversingsingle-pass fluid-to-fluid contact heat exchanger of claim 6 wherein theannular discharge member is disposed coaxially with the separator-sidesection along the flow axis thereof.
 9. The non-reversing single-passfluid-to-fluid contact heat exchanger of claim 6 wherein a coniform flowdivider is disposed axially of an exhaust-fluid discharge aperturesupplied by the said annular enveloping exhaust-fluid dischargepassageway and directed against the discharge of cooled exhaust fluidstherefrom, and means for axially advancing and retracting the saidconiform flow divider with respect to the said exhaust-fluid dischargeaperture.
 10. The non-reversing single-pass fluid-to-fluid contact heatexchanger of claim 6 wherein a plurality of receiver-side nozzle membersare disposed within the receiver-side section opposite a plurality ofcompanion separator-side discharge members disposed within theseparator-side section of said ducting chamber.
 11. The non-reversingsingle-pass fluid-to-fluid contact heat exchanger of claim 2 wherein theannular nozzle member and exhaust-fluid supply pipe of the receiver-sidesection are slidably disposed along the flow axis thereof; and means foraxially advancing or retracting said receiver-side annular nozzle memberwith respect to the leading edge of its companion oppositeseparator-side annular discharge member along the longitudinal flow axisof said contact heat exchanger.
 12. The non-reversing single-passfluid-to-fluid contact heat exchanger of claim 2 wherein the annulardischarge member and exhaust-fluid discharge pipe of the separator-sidesection are slidably disposed along the flow axis thereof; and means foraxially advancing or retracting said separator-side annular-dischargemember with respect to the trailing edge of its companion oppositereceiver-Side annular nozzle member along the longitudinal flow axis ofsaid contact heat exchanger.
 13. The non-reversing single-passfluid-to-fluid contact heat exchanger of claim 6 wherein the annularnozzle member and intake-fluid supply pipe of the receiver-side sectionare slidably disposed along the flow axis thereof; and means for axiallyadvancing or retracting said receiver-side annular nozzle member withrespect to the leading edge of its companion opposite separator-sideannular discharge member along the longitudinal flow axis of saidcontact heat exchanger.
 14. The non-reversing single-pass fluid-to-fluidcontact heat exchanger of claim 6 wherein the annular discharge memberand intake-fluid discharge pipe of the separator-side section areslidably disposed along the flow axis thereof; and means for axiallyadvancing or retracting said separator-side annular discharge memberwith respect to the trailing edge of its companion oppositereceiver-side annular nozzle member along the longitudinal flow axis ofsaid contact heat exchanger.
 15. The non-reversing single-passfluid-to-fluid contact heat exchanger of claim 6 wherein a plurality ofreceiver-side annular nozzle members and attached intake-fluid supplypipes are slidably disposed within the receiver-side section along theflow axes thereof; and means for axially advancing and retracting saidplurality of receiver-side annular nozzle members with respect to theleading edges of their respective individual opposite companion membersof a plurality of separator-side annular discharge members along thelongitudinal flow axes of said contact heat exchanger.
 16. Thenon-reversing single-pass fluid-to-fluid contact heat exchanger of claim6 wherein a plurality of separator-side annular discharge members andattached intake-fluid discharge pipes are slidably disposed within theseparator-side section along the flow axes thereof; and means foraxially advancing and retracting said plurality of separator-sideannular discharge members with respect to the trailing edges of theirrespective individual opposite companion members of a plurality ofreceiver-side annular nozzle members along the longitudinal flow axes ofsaid contact heat exchanger.
 17. The non-reversing single-passfluid-to-fluid contact heat exchanger of claim 2 wherein the elongatephenum or ducting chamber provides a slidable connection in the mid-bodythereof which permits either of the receiver-side or separator-sidesections to telescope into the other along the flow axis of the heatexchanger, and means for axially advancing or retracting either of theaforesaid receiver-side or separator-side sections to adjustcharacteristic length of the heat transfer process between the trailingedge of the receiver-side annular nozzle member and the leading edge ofthe separator-side annular discharge member.
 18. The non-reversingsingle-pass fluid-to-fluid contact heat exchanger of claim 6 wherein theelongate plenum or ducting chamber provides a slidable connection in themid-body thereof which permits either of the receiver-side orseparator-side sections to telescope into the other along the flow axisof the heat exchanger, and means for axially advancing or retractingeither of the aforesaid receiver-side or separator-side sections toadjust characteristic length of the heat transfer process between thetrailing edge of the receiver-side annular nozzle member and the leadingedge of the separator-side annular discharge member.
 19. Thenon-reversing single-pass fluid-to-fluid contact heat exchanger of claim6 wherein a plurality of receiver-side nozzle members are disposedwithin the receiver-side section opposite a plurality of companiondischarge members disposed within the separator-side section, wherebythe elongate plenum or ducting chamber provides a slidable connection inthe mid-body thereof which permits either of the receiver-side orseparator-side sections to telescope into the other along the slow axesof the heat exchanger, and meanS for axially advancing or retractingeither of the aforesaid receiver-side or separator-side sections toadjust characteristic length of the heat transfer process between thetrailing edges of the plurality of receiver-side annular nozzle membersand the leading edges of the plurality of separator-side annulardischarge members.
 20. A non-reversing single-pass fluid-to-fluidcontact heat exchanger adapted to receive and exchange energy between aplurality of fluid streams at different thermodynamic energy states inparallel flow with respect to each other; said contact heat exchangercomprising a substantially closed plenum or ducting chamber defined byside and confining walls and providing receiver-side, mixing andseparator-side sections, said mixing section disposed in said ductingchamber between the receiver-side and separator-side sections thereof; aplurality of intake-fluid nozzles each formed by configured companionpartition members disposed laterally between the sidewalls of saidreceiver-side section in spaced proximity with respect to each other andadjacent partition members and the said sidewalls so that intersticesformed therebetween divide the receiver-side section into alternateadjacent intake-fluid nozzle passageways and exhaust-fluid passagewayswhich discharge to the mixing section of said heat exchanger;intake-fluid supply conduits communicating with the nozzle passagewaysof said receiver-side section and supplying cool pressurized intakefluids thereto; exhaust-fluid supply conduits communicating with theexhaust-fluid passageways of said receiver-side section and supplyinghot low-pressure exhaust fluids thereto; whereby particles of theaforesaid intake-fluid and exhaust-fluid streams are brought intophysical contact with each other within said mixing section atsubstantially equal pressures while possessing substantially unequal andparallel and velocity vectors so as to facilitate the contactinterchange of thermal and kinetic energy therebetween; a plurality ofintake-fluid discharge members each formed by flow-dividing companionpartition members disposed laterally between the sidewalls of saidseparator-side section in spaced proximity with respect to each otherand adjacent companion partition members and the said sidewalls so thatinterstices formed therebetween divide the separator-side section intoalternate adjacent intake-fluid and exhaust-fluid passageways disposedopposite their respective companion intake-fluid and exhaust-fluidpassageways of the receiver-side section; whereby the contactingintake-fluid and exhaust-fluid streams leaving the said mixing sectionmay enter their respective intake-fluid and exhaust-fluid passageways ofthe separator-side section and flow towards discharge outlets of saidcontact heat exchanger; intake-fluid discharge conduits communicatingwith the intake-fluid discharge passageways of said separator-sidesection and receiving heated intake fluids therefrom; and exhaust-fluiddischarge conduits communicating with the exhaust-fluid dischargepassageways of said separator-side section and receiving cooled exhaustfluids therefrom.
 21. The non-reversing single-pass fluid-to-fluidcontact heat exchanger of claim 20 wherein the receiver-side partitionmembers define a single nozzle passage disposed centrally with thecentral longitudinal flow plane of the heat exchanger.
 22. Thenon-reversing single-pass fluid-to-fluid contact heat exchanger of claim20 wherein the separator-side partition members define a singleintake-fluid discharge passageway disposed centrally with the centrallongitudinal flow plane of the heat exchanger.
 23. A non-reversingsingle-pass fluid-to-fluid contact heat exchanger adapted to receive andexchange energy between a plurality of fluid streams at differentthermodynamic energy states in parallel flow with respect to each other;said contact heat exchanger comprising a substantially closed plenum orducting chamber defined by side and confining walls and providingreceiveR-side, mixing and separator-side sections, said mixing sectiondisposed in said ducting chamber between the receiver-side andseparator-side sections thereof; a plurality of partition members havingspaced proximity with respect to each other and the sidewalls of saidreceiver-side section and disposed laterally between the said sidewallsso that interstices formed therebetween divide the receiver-side sectioninto alternate adjacent intake-fluid and exhaust-fluid passageways whichdischarge to the mixing section of said heat exchanger; a fluid pump orfan disposed to supply pressurized intake fluids; intake-fluid supplyconduits communicating with the discharge of said fluid pump or fan andthe individual intake-fluid passageways of the said receiver-sidesection; an intake-fluid nozzle passageway disposed in the supplyconduit branch for each individual intake-fluid passageway of the saidreceiver-side section and discharging high-velocity intake fluidsthereto; exhaust-fluid supply conduits communicating with theexhaust-fluid passageways of said receiver-side section and supplyinghot low-velocity exhaust fluids thereto; whereby particles of theaforesaid intake-fluid and exhaust-fluid streams are brought intophysical contact with each other within said mixing section atsubstantially equal presssures while possessing substantially unequaland parallel velocity vectors so as to facilitate the contactinterchange of thermal and kinetic energy therebetween; a plurality offlow-dividing partition members having spaced proximity with respect toeach other and the sidewalls of said separator-side section and disposedlaterally between the said sidewalls so that interstices formedtherebetween divide the separator-side section into alternate adjacentintake-fluid and exhaust-fluid passageways disposed opposite theirrespective companion intake-fluid and exhaust-fluid passageways of thereceiver-side section; whereby the contacting intake-fluid andexhaust-fluid streams leaving the said mixing section may enterintake-fluid discharge conduits communicating with the intake-fluiddischarge passageways of said separator-side section and receivingheated intake fluids therefrom; and exhaust-fluid discharge conduitscommunicating with the exhaust-fluid discharge passageways of saidseparator-side section and receiving cooled exhaust fluids therefrom.24. A non-reversing single-pass fluid-to-fluid contact heat exchangeradapted to receive and exchange energy between a plurality of fluidstreams at different thermodynamic energy states in parallel flow withrespect to each other; said contact heat exchanger comprising asubstantially closed plenum or ducting chamber defined by side andconfining walls and providing receiver-side, mixing and separator-sidesections, said mixing section disposed in said ducting chamber betweenthe receiver-side and separator-side sections thereof; a plurality ofpartition members having spaced proximity with respect to each other andthe sidewalls of said receiver-side section and disposed laterallybetween the said sidewalls so that interstices formed therebetweendivide the receiver-side section into alternate adjacent intake-fluidand exhaust-fluid passageways which discharge to the mixing section ofsaid heat exchanger; a fluid pump or fan disposed to supplyhigh-velocity intake fluids; intake-fluid supply conduits communicatingwith the discharge of said fluid pump or fan and the individualintake-fluid passageways of the said receiver-side section;exhaust-fluid supply conduits communicating with the exhaust-fluidpassageways of said receiver-side section and supplying hot low-velocityexhaust fluids thereto; whereby particles of the aforesaid intake-fluidand exhaust-fluid streams are brought into physical contact with eachother within said mixing section at substantially equal pressures whilepossessing substantially unequal and parallel velocity vectors so as tofacilitate the contact interchange of thermal and kinetic energytherebetween; a plurality of flow-dividing partition members havingspaced proximity with respect to each other and the sidewalls of saidseparator-side section and disposed laterally between the said sidewallsso that interstices formed therebetween divide the separator-sidesection into alternate adjacent intake-fluid and exhaust-fluidpassageways disposed opposite their respective companion intake-fluidand exhaust-fluid passageways of the receiver-side section; whereby thecontacting intake-fluid and exhaust-fluid streams leaving the saidmixing section may enter their respective intake-fluid and exhaust-fluidpassageways of the separator-side section and flow towards dischargeoutlets of said contact heat exchanger; intake-fluid discharge conduitscommunicating with the intake-fluid discharge passageways of saidseparator-side section and receiving heated intake-fluids therefrom; andexhaust-fluid discharge conduits communicating with the exhaust-fluiddischarge passageways of said separator-side section and receivingcooled exhaust fluids therefrom.
 25. The non-reversing single-passfluid-to-fluid contact heat exchanger of claim 2 wherein a coniform flowdivider is disposed axially of a duct throat section within theintake-fluid discharge ductwork of said contact heat exchanger andsupplied from the said annular intake-fluid discharge passageway of theseparator-side section, the said coniform flow divider being directedagainst the discharge of heated intake fluids therefrom, and means foraxially advancing and retracting the said coniform flow divider withrespect to the said intake-fluid discharge throat section.
 26. Thenon-reversing single-pass fluid-to-fluid contact heat exchanger of claim6 wherein a coniform flow divider is disposed axially of a duct throatsection within the intake-fluid discharge ductwork of said contact heatexchanger and supplied from the said central intake-fluid dischargepassageway of the separator-side siection, the said coniform flowdivider being directed against the discharge of heated intake fluidstherefrom, and means for axially advancing and retracting the saidconiform flow divider respect to the said intake-fluid discharge throatsection.